CN102777592B - Double clutch transmission - Google Patents
Double clutch transmission Download PDFInfo
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- CN102777592B CN102777592B CN201210137885.0A CN201210137885A CN102777592B CN 102777592 B CN102777592 B CN 102777592B CN 201210137885 A CN201210137885 A CN 201210137885A CN 102777592 B CN102777592 B CN 102777592B
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- valve
- pressure
- blocking device
- pipeline
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
- F16D25/14—Fluid pressure control
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D48/0206—Control by fluid pressure in a system with a plurality of fluid-actuated clutches
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/0021—Generation or control of line pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/68—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings
- F16H61/684—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive
- F16H61/688—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive with two inputs, e.g. selection of one of two torque-flow paths by clutches
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
- F16H63/34—Locking or disabling mechanisms
- F16H63/3416—Parking lock mechanisms or brakes in the transmission
- F16H63/3483—Parking lock mechanisms or brakes in the transmission with hydraulic actuating means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D2048/0227—Source of pressure producing the clutch engagement or disengagement action within a circuit; Means for initiating command action in power assisted devices
- F16D2048/0233—Source of pressure producing the clutch engagement or disengagement action within a circuit; Means for initiating command action in power assisted devices by rotary pump actuation
- F16D2048/0236—Source of pressure producing the clutch engagement or disengagement action within a circuit; Means for initiating command action in power assisted devices by rotary pump actuation with multiple independent pumps, e.g. one per clutch, or for supplying fluid to different systems
- F16D2048/0242—Two or more rotating pumps driven together by the same power source, e.g. connected by a shaft, or a single pump having two or more fluid outputs
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D2048/0257—Hydraulic circuit layouts, i.e. details of hydraulic circuit elements or the arrangement thereof
- F16D2048/0281—Complex circuits with more than two valves in series or special arrangements thereof not provided for in previous groups
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D2048/0257—Hydraulic circuit layouts, i.e. details of hydraulic circuit elements or the arrangement thereof
- F16D2048/0287—Hydraulic circuits combining clutch actuation and other hydraulic systems
- F16D2048/029—Hydraulic circuits combining clutch actuation with clutch lubrication or cooling
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D2048/0257—Hydraulic circuit layouts, i.e. details of hydraulic circuit elements or the arrangement thereof
- F16D2048/0287—Hydraulic circuits combining clutch actuation and other hydraulic systems
- F16D2048/0293—Hydraulic circuits combining clutch and transmission actuation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
- F16H61/0202—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric
- F16H61/0204—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal
- F16H61/0206—Layout of electro-hydraulic control circuits, e.g. arrangement of valves
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Control Of Transmission Device (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Gear-Shifting Mechanisms (AREA)
Abstract
The invention relates to a clutch transmission, especially to a double clutch transmission, used for vehicles, especially for motor vehicles. The clutch transmission comprises at least one shifted transmission and a hydraulic circuit, the shifted transmission has hydraulically operated clutches and at least one hydraulically operable gear actuators, and the hydraulic circuit comprises a storage tank supplying no-pressure hydraulic medium and a pressure source supplying a hydraulic medium loaded pressure; wherein first pressure regulating valves (101,101')are connected respectively before the corresponding clutches for operating the corresponding clutches, and at least one second pressure regulating valve (141) is connected before a corresponding gear regulator; wherein at least one of the pressure regulating valves (101,101',104)is connected with a conversion device connected before, and the conversion device enables at least one pressure regulating valve and a hydraulically operated parking locking device to be connected with either the pressure source or the storage tank.
Description
Technical field
The present invention relates to a kind of clutch speed-changer, especially dual-clutch transmission, for vehicle, in particular for Motor Vehicle, described clutch speed-changer has at least one shift transmission, described shift transmission comprises the clutch of hydraulically operable and the gear regulator of at least one hydraulically operable, described clutch speed-changer has oil hydraulic circuit, and described oil hydraulic circuit comprises the pressure source providing the storage tank of stress-free hydraulic medium and provide the hydraulic medium being loaded pressure.
Background technique
Dual-clutch transmission preferably uses in car.Dual-clutch transmission has two transmission input shafts arranged coaxially toward each other usually, and described transmission input shaft configures respectively to the shift transmission being also referred to as sub-speed changer in the case.All configure clutch to transmission input shaft is one of any, the transmission input shaft of corresponding shift transmission is coupled with motor, the preferably output of the internal-combustion engine of Motor Vehicle in locking manner by described clutch engagement force.The first shift transmission in two shift transmissions typically comprises odd gear, and the second sub-speed changer in sub-speed changer comprises even gear and backing car gear.Simple clutch speed-changer generally includes only a clutch and only a shift transmission, by whole gears of the convertible clutch speed-changer of described shift transmission.
Typically, during travelling, one of shift transmission works, and this means, configures and is coupled with motor to the clutch of this transmission input shaft by configuration to the transmission input shaft of this shift transmission.In the shift transmission of work, a gear is linked into, and this gear provides current transmission ratio.Control gear is tried to achieve: whether will be linked into a higher gear or a lower gear according to running condition.The gear that described expectation uses as next gear is linked in idle second shift transmission.So, in order to convert gear, the clutch of idle shift transmission being closed, and the clutch of the shift transmission of work is opened.The clutch of the shift transmission of preferred work to open with the clutch of idle shift transmission closed overlapping like this, make the live axle from motor to Motor Vehicle only interrupt power stream a little.Transforming gear as a result, the shift transmission of Previous work does not work, and previous idle shift transmission becomes the shift transmission of work.Then can be linked in present idle sub-speed changer and estimate as the gear needed for the next one.
Being linked into and exiting by element, carry out preferably by gear shift ail of gear, described gear shift ail by oil hydraulic cylinder namely before the so-called shifting cylinder mentioned operate.Oil hydraulic cylinder is preferably configured as beidirectional oil hydraulic cylinder, especially synchronized cylinder or differential cylinder, thus, can give each shifting cylinder preferred disposition two gears.As an alternative solution, the oil hydraulic cylinder of single effect also can be set.Gear adjustment cylinder is also referred to as to the oil hydraulic cylinder that element, especially gear shift ail operate.Especially the gear adjustment cylinder being configured to synchronized cylinder being configured with two gears preferably has three dislocations, wherein, thus, in the first dislocation, be linked into one determine gear, in the second dislocation, be linked into another determine gear, described in the 3rd dislocation, two gears are not linked into.
Also hydraulically operate, namely close and open configuration in other words to the clutch of two shift transmissions.Preferably when clutch is loaded hydraulic pressure, described clutch closes respectively, and when not applying hydraulic pressure, when configure to corresponding clutch be also referred to as the oil hydraulic cylinder unloading pressure of clutch cylinder as previously mentioned time, described clutch is opened.
In addition, the working method of dual-clutch transmission itself is known, therefore, inquires into no longer in detail at this.
The structure preferably illustrated in present subject matter or in being also suitable for above paragraph in conjunction with present subject matter and the working method described there.
As described, clutch speed-changer not only obtains controlling adjusted but also cooled in other words by oil hydraulic circuit.Described oil hydraulic circuit in other words its assembly and the method that is associated with it is present subject matter.
In addition, the transmission for vehicles with so-called parking blocking device is known, and described parking blocking device makes speed changer locking when corresponding operating and especially makes the driving wheel locking of vehicle thus.Parking blocking device usually can motor or hydraulic operation.
German laid-open document DE19625019A1 discloses the corresponding system of transmission for vehicles, and described system has exercisable parking blocking device.By the also known a kind of oil hydraulic circuit for dual-clutch transmission of DE2004033362B4, described dual-clutch transmission comprises two clutches, connect a pressure regulator valve before described clutch respectively.Be provided with relief valve in parallel relative to pressure regulator valve, described relief valve is loaded the hydraulic medium of pressure to the supply of parking blocking device when operating.
Summary of the invention
The object of the invention is to, provide a kind of dual-clutch transmission, described dual-clutch transmission improves efficiency and the ability to work of oil hydraulic circuit when input is little and the number of component is few.
The present invention based on object realized by the clutch speed-changer with claim 1 feature.Clutch speed-changer according to the present invention has advantage: at least one subfunction automatically changing at least one sub-loop of oil hydraulic circuit and/or clutch speed-changer dual-clutch transmission in other words when operating parking blocking device together.Therefore, major advantage is, when being linked into parking blocking device, at least one subfunction automatically deexcitation of dual-clutch transmission, thus, especially can save energy, and on the other hand, the reliability of clutch speed-changer improves.For this reason, propose according to the present invention, before the clutch of described correspondence, connect the first pressure regulator valve respectively to operate corresponding clutch and before the gear regulator of correspondence, connect at least one second pressure regulator valve, wherein, described pressure regulator valve one of is at least connected with the conversion equipment be connected to above, and described conversion equipment makes at least one pressure regulator valve described with the parking blocking device of hydraulically operable or is connected with pressure source or with storage tank.Namely propose, be connected to after pressure regulator valve before clutch and/or gear regulator one of is at least connected to conversion equipment, wherein, conversion equipment is also connected with parking blocking device.This particularly preferably parking blocking device and corresponding pressure regulator valve be connected to conversion equipment identical connecting end on or there is the public supply pipeline being in conversion equipment downstream.By carrying out pressure-loaded to parking blocking device hydraulic medium, described parking blocking device unclamps and exits in other words.Realize thus: make when being linked into parking blocking device at least one pressure regulator valve described also automatically change without pressure and make the function deexcitation that adjusts thus thus.If before pressure regulator valve is such as connected to gear regulator, then automatically no longer gives the gearshift mechanism supply hydraulic medium of speed changer when being linked into parking blocking device, thus, no longer can carry out the adjustment of gear by means of gear regulator.But this neither be definitely required or useful in state in being linked into of Parking Brake.Namely save energy as follows by operation parking blocking device thus: gear regulator need not be supplied to hydraulic medium again and pressure source, especially can correspondingly reduce the power of the pump of hydraulic medium on-load pressure simultaneously.
Preferably the first pressure regulator valve and/or the second pressure regulator valve are connected with conversion equipment.As described, when being linked into parking blocking device, make gear adjusting apparatus deexcitation preferably by making the second pressure regulator valve be connected with conversion equipment.As an alternative solution, preferably the first pressure regulator valve or the first pressure regulator valve one of are at least connected with conversion equipment, thus, make one or two clutch change without pressure when being linked into parking blocking device simultaneously.Particularly preferably the first pressure regulator valve is connected with conversion equipment with at least one second pressure regulator valve described, thus, for transmitting the whole transmission pressure system deactivation of driving torque.If oil hydraulic circuit also comprises the sub-loop for cooling dual-clutch transmission, then described oil hydraulic circuit can continue to run, wherein, so not only need the power reduced in cooling but also in delivery hydraulic pressure medium.
A favourable expanded configuration according to the present invention proposes, conversion equipment has at least one first changing valve, described first changing valve is connected with pressure regulator valve on the first connecting end, and the second connecting end is connected with pressure source, and the 3rd connecting end is connected with storage tank.Preferred changing valve is configured to two-position three way changing valve, and thus, described changing valve can occupy two limit positions ultimate state in other words.Preferred described changing valve makes parking blocking device be connected with storage tank with corresponding pressure regulator valve in the first ultimate state, thus, described parking blocking device and corresponding pressure regulator valve are changed without pressure, described changing valve makes parking blocking device be connected with pressure source with corresponding pressure regulator valve in the second ultimate state, thus, parking blocking device exits and pressure regulator valve is supplied to the hydraulic medium being loaded pressure.
Preferably the first connecting end of the first changing valve is also connected with parking blocking device.For this reason, the first connecting end has two output terminals or leads in public supply pipeline, and described supply pipeline not only leads to parking blocking device but also leads to corresponding pressure regulator.
Propose as an alternative solution, conversion equipment has the second changing valve, and described second changing valve is connected with pressure source, storage tank and parking blocking device, and wherein, the second changing valve configures to the first changing valve as pilot valve.Therefore, according to this form of implementation, conversion equipment comprises two changing valves, and wherein, a changing valve is connected directly between pressure source and pressure regulator valve, and another second changing valve is used as pilot valve.Second changing valve is directly arranged for operation parking blocking device thus individually.Before second changing valve is connected to the first changing valve as pilot valve, thus, also the first changing valve is operated by operating the second changing valve, described first changing valve is connected with corresponding pressure regulator valve again, thus, such as change the second changing valve to corresponding pressure regulator valve supply hydraulic medium in order to exit parking blocking device by operation second changing valve simultaneously.Realize thus: the electric actuator for controlling the first changing valve can be cancelled.In addition realize: two valves and changing valve and pressure regulator valve can construct optimum for the task of its correspondence thus.Preferably the second changing valve is also configured to two-position three way changing valve.Also can consider, changing valve one of is at least configured to Proportional valve.
Particularly preferably propose, the changing valve be at least connected with parking blocking device i.e. the first changing valve or the second changing valve to be connected with parking blocking device depending on which in both and to have Returnning spring, changing valve squeezes in its first ultimate state by described Returnning spring, in described first ultimate state, parking blocking device is changed be connected with storage tank without pressure in order to it.Returnning spring is thus for making changing valve arrive in home, and in described home, such as when operating current interrupts, parking blocking device can not exit, or is linked into.Preferred parking blocking device has the operations actuator of hydraulic pressure and Electromagnetically activated locking mechanism, the operations actuator of described hydraulic pressure is connected with corresponding changing valve, and described locking mechanism makes parking blocking device preferable shape remain in locking manner in its state exited.So, in fact whether parking blocking device be linked into when hydraulic medium is cancelled, depend on whether locking mechanism discharges parking blocking device, wherein, parking blocking device meets the reseat pressure that destination opposing produces preferably by the spring element of machinery and squeezes in the position be linked into.
A favourable expanded configuration according to the present invention proposes, and at least one second pressure regulator valve described is directly connected with pressure source.Namely propose at this, the operation of gear regulator and parking blocking device is independently also supplied to hydraulic medium, and its mode is that the second pressure regulator valve is directly connected with pressure source.For this reason, the second pressure regulator valve is such as connected with such connecting end of changing valve: pressure source is also connected on this connecting end.As an alternative solution, from the corresponding pressure piping of pressure source can separate one lead to changing valve in other words the pipeline of conversion equipment and another lead to the pressure piping of the second pressure regulator valve.Preferably be interpreted as at least one pump for pressure source in the current situation, described pump is particularly preferably driven by motor, and thus, pump power does not rely on the rotating speed of the internal-combustion engine that can be connected with clutch speed-changer effect.If configure to two of clutch the first pressure regulator valves and conversion equipment in other words changing valve be connected, then when operating Parking Brake, preferred at least clutch is changed without pressure, avoid power to pass to speed changer from internal-combustion engine thus, but gear adjustment process can be performed in the transmission.
(the first or second) changing valve be particularly preferably at least connected with parking blocking device is additional to Returnning spring or has at least one valve face as its alternative, and described valve face is connected with pressure source to regulate pressure.At this, construct corresponding changing valve like this, when making the pressure when pressure source exceed determined value, changing valve is displaced in its ultimate state, and in described ultimate state, parking blocking device is connected with storage tank.Such as parking blocking device can be protected in order to avoid excess pressure thus.
Preferably propose in addition, pressure source comprise at least one can motor drive/by the pressure accumlator of motor-driven pump and/or at least one hydraulic pressure.Pressure source, especially pump and/or pressure accumlator preferably by supply pipeline in other words pressure piping be especially connected with the first and/or second changing valve of conversion equipment with conversion equipment as mentioned above.
A favourable expanded configuration according to the present invention proposes, and the changing valve is at least connected with parking blocking device makes pressure source, especially pressure accumlator be connected with storage tank, if parking blocking device also with store up tank connected words.Realize thus: when being linked into parking blocking device, pressure accumlator is emptying, and must desirably exit parking blocking device.
Accompanying drawing explanation
The present invention to be described in detail below by means of accompanying drawing.Accompanying drawing represents:
The explanatory view of Fig. 1 oil hydraulic circuit,
The expanded configuration that of Fig. 2 oil hydraulic circuit is favourable,
An advantageous scheme of the oil hydraulic circuit that Fig. 3 constructs further,
Fig. 4 for operating the conversion equipment of the oil hydraulic circuit of the Parking Brake according to an embodiment as an alternative solution,
One of Fig. 5 oil hydraulic circuit favourable expanded configuration as an alternative solution, and
An advantageous scheme of the configuration as an alternative solution of Fig. 6 oil hydraulic circuit.
Reference numerals list:
1 oil hydraulic circuit
3 storage tanks
5 motor
7 first pumps
9 second pumps
11 resolution elements
13 pipelines
15 pipelines
17T shape section
19 pipelines
21 suction filters
23 pipelines
25 branches
27 pressure limiting valves
29 pipelines
31 filter-presses
33 connecting ends
35 changing valves
37 bypasses
39 pressure difference valve
41 connecting ends
43 connecting ends
45 connecting ends
47 connecting ends
49 pipelines
51 safety check
53 pressure accumlators
55 pressure-detecting devices
57 pipelines
59 hydraulic subsidiary loops
61 pipelines
63 pipelines
65 valve faces
67 valve faces
69 pipelines
71 branches
73 pipelines
74 pressure pipings
75 branches
77 branches
79 branches
81 pipelines
83 pipelines
85 pipelines
87 sub-speed changer loops
89 connecting ends
91 changing valves
91 ' changing valve
93 connecting ends
95 connecting ends
97 pipelines
99 connecting ends
101 pressure regulator valves
101 ' pressure regulator valve
103 connecting ends
105 pipelines
107 connecting ends
109 pipelines
111 safety check
113 branches
115 pipelines
117 branches
119 pressure-detecting devices
121 pilot valves
121 ' pilot valve
123 controller for electric consumption
125 connecting ends
127 connecting ends
129 connecting ends
131 pipelines
133 branches
135 pipelines
137 valve faces
139 sub-speed changer loops
141 pressure regulator valves
143 pipelines
145 branches
147 pipelines
149 pipelines
151 branches
153 pipelines
155 gear adjustment cylinders
155 ' gear adjustment cylinder
157 gear adjustment cylinders
157 ' gear adjustment cylinder
159 volume control valves
159 ' volume control valve
161 connecting ends
163 connecting ends
165 connecting ends
167 connecting ends
169 chambeies
171 chambeies
173 pistons
175 branches
177 pipelines
179 volume control valves
179 ' volume control valve
181 pipelines
183 coolers
185 volume control valves
187 branches
189 pipelines
191 pressure limiting valves
193 branches
195 bypasses
197 pressure difference valve
199 connecting ends
201 connecting ends
203 connecting ends
205 connecting ends
207 connecting ends
209 pipelines
211 branches
213 pipelines
215 filter-presses
217 bypasses
219 pressure difference valve
221 cooling units
223 cooling units
225 sub-loops
227 parking blocking devices
229 final controlling element
231 cylinders
233 pistons
235 parking blocking elements
237 holding members
239 holding devices
241 electromagnets
243 locking mechanisms
245 Returnning springs
247 conversion equipments
249 pressure sources
251 changing valves
253 connecting ends
255 connecting ends
257 connecting ends
259 filter-presses
261 pipelines
263 pipelines
265 filter-presses
267 connecting ends
269 changing valves
271 connecting ends
273 connecting ends
275 connecting ends
277 filter-presses
279 pipelines
281 pipelines
283 valve faces
285 pipelines
K1 clutch
K2 clutch
Embodiment
Fig. 1 shows an oil hydraulic circuit 1, and described oil hydraulic circuit is used for operating dual clutch device speed changer, especially engages and be linked into and exit gear and cool described dual-clutch transmission.Oil hydraulic circuit 1 comprises storage tank 3, and described storage tank especially uses as the tank or oil sump that are used for hydraulic medium, and described hydraulic medium is used for operation and cooling, and hydraulic medium is preferably stored in described storage tank without pressure.Be provided with motor 5, described motoring first pump 7 and the second pump 9.Motor 5 preferably can control in its rotating speed and sense of rotation, particularly preferably adjustable.First pump 7 is permanently connected, namely without the need to arranging resolution element with motor 5.This means, pump 7 is driven all the time when motor 5 operates and hydraulic medium is preferred in both rotational directions through being transferred reversingly.Pump 9 is connected with motor 5 preferably by resolution element 11.Namely can be: pump 9 and motor 5 take off coupling, and the described pump when motor 5 operates is not operated.By pump 9 delivery hydraulic pressure medium also whether resolution element 11 is preferably configured as coupling or is configured to lost motion device, and wherein, the sense of rotation in the latter case by motor 5 is determined: to be.
The branch 17 that first pump 7 passes into respectively by pipeline 13,15 and another pipeline 19 with the second pump 9 is connected.Another pipeline described makes storage tank 3 be connected with branch 17 by suction filter 21.Thus, in general, pump 7,9 entrance by pipeline 13,15, branch 17 is connected with storage tank 3 with the pipeline 19 with suction filter 21.
The outlet of the first pump 7 is connected with the pipeline 23 leading to branch 25.Branch 25 is connected with storage tank 3 by pressure limiting valve 27.Pressure limiting valve 27 can be opened towards the direction of storage tank 3 when overvoltage.In addition, from branch 25 pass-out pipeline 29, described pipeline leads to the connecting end 33 of changing valve 35 by filter-press 31.
Filter-press 31 can be bypassed 37 cross-over connections, wherein, is provided with pressure difference valve 39 in bypass 37, and described pressure difference valve can realize the direction cross-over connection filter 31 towards connecting end 33 when overvoltage.Opening of pressure difference valve 39 is carried out from the predetermined pressure reduction by filter-press 31.
Changing valve 35 is configured to two-position five-way valve, and described two-position five-way valve also has other four connecting ends 41,43,45,47 except connecting end 33.In the first shown in FIG transition status of changing valve 35, connecting end 33 is connected with connecting end 41, and other connecting end 43,45 and 47 is changed obstructed, namely closes.Connecting end 41 leads in pipeline 49, is provided with safety check 51 in described pipeline.Pipeline 49 leads to pressure accumlator 53, wherein, before pressure accumlator 53, and pressure-detecting device 55 and pipeline 49 hydraulic connecting.
In second transition status can known from Fig. 1 of changing valve 35, connecting end 33 is connected with the connecting end 43 led in pipeline 57, and described pipeline leads to hydraulic subsidiary loop 59, and described hydraulic subsidiary loop is in particular for cooling the clutch of dual-clutch transmission.In described second transition status, connecting end 41 changes obstructed and connecting end 45 is connected with connecting end 47.At this, pipeline 61 leads in connecting end 45, and described pipeline is loaded the pressure of the hydraulic medium in pressure accumlator 53.Connecting end 47 leads in pipeline 63, the first valve face 65 hydraulic connecting of described pipeline and changing valve 35.Second valve face 67 of changing valve 35 by pipeline 69 by the pressure of on-load pressure storage 53 constantly.
Punish out pipeline 73 from pipeline 49 in branch 71, branch 75, separate pipeline 61 again from described pipeline and separate pipeline 69 in branch 77.Branch 71 is connected on described safety check in the side deviating from changing valve 35 of safety check 51.
Pipeline 73 leads in branch 79, from described branch pass-out pipeline 81,83 and 85.
Pipeline 81 leads in the sub-speed changer loop 87 for supplying the first sub-speed changer.First sub-speed changer has clutch K1.Pipeline 81 leads in the connecting end 89 of changing valve 91, and described changing valve is configured to two position three-way valve, and uses as the safety valve for clutch K1.In the first transition status shown in changing valve 91, connecting end 89 and connecting end 93 hydraulic connecting, and the connecting end 95 of changing valve 91 is changed obstructed.In second transition status can known from Fig. 1 of changing valve 91, connecting end 93 is connected with connecting end 95 and is connected with storage tank 3 by this connecting end, and connecting end 89 is changed obstructed.As then known, in described second transition status, clutch K1 changes without pressure.
Connecting end 93 is connected with pipeline 97 and is connected with the connecting end 99 of pressure regulator valve 101 by this pipeline.Pressure regulator valve 101 is configured to two-position three-way proportional valve, and described two-position three-way proportional valve has connecting end 103, and described connecting end is connected with clutch K1 by pipeline 105.In addition, pressure regulator valve 101 has connecting end 107, and described connecting end is connected with storage tank 3.In the first ultimate state of pressure regulator valve 101, connecting end 99 is connected with connecting end 103, and connecting end 107 is changed obstructed.In the case, the whole pressure be present in pipeline 97 of hydraulic medium act on clutch K1.In the second ultimate state, connecting end 103 is connected with connecting end 107, and thus, clutch K1 is without pressure.By the proportional change between these ultimate states, pressure regulator valve 101 regulates the pressure be present in clutch K1 in a per se known way.Pipeline 109 gets back to pipeline 97 from clutch K1 by safety check 111 is logical.If the pressure increase in clutch K1 exceedes the pressure in pipeline 97, then safety check 111 is opened, and thus, clutch K1 is released by the hydraulic connecting between pipeline 109 and pipeline 97.Branch 113, separate a pipeline 115 from pipeline 109, the pressure in clutch K1 is returned to pressure regulator valve 101 as adjustable parameter by described pipeline.
In pipeline 105, be provided with branch 117, pressure-detecting device 119 acts on connection by described branch on hydraulic pressure.In this way, the pressure be present in clutch K1 is detected by pressure-detecting device 119.
Changing valve 91 is controlled by pilot valve 121.Described pilot valve is operated by electric actuator 123.Described pilot valve is configured to two position three-way valve and comprises connecting end 125,127 and 129.Connecting end 125 is connected with the branch 133 be arranged in pipeline 81 by pipeline 131.Connecting end 127 is connected with the valve face 137 of changing valve 91 by pipeline 135.In first transition status shown here of pilot valve 121, connecting end 125 is changed obstructed, and connecting end 127 is connected with connecting end 129 and be connected with storage tank 3 by this connecting end, thus, the valve face 137 of changing valve 91 is changed without pressure by pipeline 135.When there is not electric control signal on final controlling element 123, preferred pilot valve 121 occupies this transition status.In second transition status occupied of pilot valve 121, connecting end 125 is connected with connecting end 127, and connecting end 129 is changed obstructed.In the case, the pressure be present in pipeline 81 acts on the valve face 137 of changing valve 91 by branch 133, pipeline 131 and pipeline 135, thus, described changing valve opposing pre-tensioning is transformed in its second transition status, in described second transition status, connecting end 93 and connecting end 95 hydraulic connecting, thus, clutch K1 changes without pressure.Namely can operation transformation valve 91 like this preferably by electric control pilot valve 121, make clutch K1 change without pressure and open thus.
The pipeline 83 of drawing from branch 79 supplies for the clutch K2 of the sub-oil hydraulic circuit 139 to the second sub-speed changer.The control section of clutch K2 also comprises changing valve 91 ', pilot valve 121 ' and pressure regulator valve 101 '.Working method is identical with the working method described in conjunction with first clutch K1.For this reason, corresponding description is not carried out in antithetical phrase speed changer loop 87.The hydraulic control of clutch K2 is corresponding to the hydraulic control of clutch K1.
The pipeline 85 of drawing from branch 79 is connected with pressure regulator valve 141, and the pressure of the hydraulic medium in pipeline 143 regulates by described pressure regulator valve.The working method of pressure regulator valve 141 is preferably corresponding to the working method of pressure regulator valve 101,101 ', thus at this without the need to redescribing.Pipeline 143 is connected with branch 145, draws pipeline 147 and pipeline 149 from described branch.In pipeline 149, be provided with branch 151, draw pipeline 153 from described branch, by described pipeline, be present in pipeline 149 and the pressure be present in thus in pipeline 143 can be used as adjustable parameter and returns to pressure regulator valve 141.Clearly, branch 151 also can be arranged in pipeline 151 or 147.
Pipeline 147 supplies for the gear regulator 155 and 157 in antithetical phrase speed changer loop 87, and described gear regulator is configured to beidirectional cylinder, i.e. synchronized cylinder.
In order to hydraulic control gear regulator 155, be provided with volume control valve 159, described volume control valve is configured to 3-position 4-way Proportional valve.Described volume control valve has four connecting ends 161,163,165 and 167.First connecting end 161 is connected with pipeline 147, and the second connecting end 163 is connected with the first chamber 169 of gear regulator 155, and the 3rd connecting end 165 is connected with the second chamber 171 of gear regulator 155, and the 4th connecting end 167 is connected with storage tank 3.In the first ultimate state of volume control valve 159, the first connecting end 161 is connected with the second connecting end 163, and the 3rd connecting end 165 is connected with the 4th connecting end 167.In the case, hydraulic medium can flow to the first chamber 169 of gear regulator 155 from pipeline 147, and the second chamber 171 by connecting end 165,167 change towards storage tank 3 without pressure.In this way, the piston 173 of gear regulator 155 moves in a first direction, so that the determination gear such as exiting dual-clutch transmission is linked into another in other words determine gear.
In the second ultimate state of volume control valve 159, not only connecting end 163 but also connecting end 165 are connected with connecting end 167, and wherein, connecting end 161 is changed obstructed.In this way, two chambeies 169,171 of gear regulator 155 are connected with storage tank 3, and thus, described chamber is changed without pressure.So the piston 173 of gear regulator 155 is stayed only in its instantaneous position, because do not have masterpiece to be used on described piston.
In the 3rd ultimate state of volume control valve 159, connecting end 161 is connected with connecting end 165, and connecting end 163 is connected with connecting end 167.In the case, hydraulic medium flow to the second chamber 171 of gear regulator 155 from pipeline 147, the first chamber 169 by connecting end 163 and connecting end 167 change towards storage tank 3 without pressure.So hydraulic medium applies power like this on the piston 173 of gear regulator 155, described piston is shifted in a second direction that is opposite the first direction.In this way, previously mentioned described another determines that gear can exit mention in other words described and determine that gear is linked into.
As described, volume control valve 159 is configured to Proportional valve.Hydraulic medium from pipeline 147 flows through the change of valve state between three ultimate states and distributes to chamber 169,171, thus, being linked into of predetermined gear can exit process constant speed degree really in other words by control/adjusted volume stream.
Branch 175, separate a pipeline 177 from pipeline 147, described pipeline leads in volume control valve 179, and described volume control valve is for controlling gear regulator 157.The working method of hydraulic control gear adjustment cylinder 157 is identical with the working method described in conjunction with gear regulator 155.Therefore without the need to redescribing.
Pipeline 149 supplies for the gear regulator 155 ' and 157 ' of the second sub-speed changer in antithetical phrase speed changer loop 139.In order to control described gear regulator, be also provided with volume control valve 159 ' and 179 '.Sub-speed changer loop 87 with 139 with regard to gear regulator 155,155 ' in other words 157,157 ' control with regard to construct identical, therefore with reference to description above.
The outlet of pump 9 is connected with pipeline 181, and described pipeline leads to hydraulic subsidiary loop 59, and described hydraulic subsidiary loop is preferably in particular for cooled clutch K1, K2.Pipeline 181 leads to volume control valve 185 by cooler 183.After the outlet of pump 9 and before cooler 183, in pipeline 181, be provided with branch 187, separate from described pipeline one leads to storage tank 3 pipeline 189 by the pressure limiting valve 191 opened towards the direction of storage tank 3.After branch 187, before cooler 183, be provided with branch 193, draw from changing valve 35 and the pipeline 57 be connected with the connecting end 43 of described changing valve leads to described branch.When changing valve 35 is in its second transition status, can supply to hydraulic subsidiary loop 59 hydraulic medium carried by pump 7 by pipeline 57.In addition, separate bypass 195 from branch 193, described bypass has pressure difference valve 197 and in parallel with cooler 183.Pressure difference valve 197 discharges bypass when overvoltage towards the direction of volume control valve 185.In this way, cooler 183 can by cross-over connection.
Volume control valve 185 is configured to 3-position 4-way Proportional valve, and described 3-position 4-way Proportional valve has connecting end 199,201,203,205 and 207.Connecting end 199 and pipeline 181 by cooler 183 in other words pressure difference valve 197 be connected, also, this connecting end is connected with pipeline 181 with branch 211 by pipeline 209 connecting end 201.That is, because connecting end 199 is connected in cooler 183 downstream with pipeline 181 with 201, so described connecting end forms the public connecting end of volume control valve 185.Just depict two connecting ends 199,201 for knowing reason, but in fact a connecting end such as 199 or 201 is only set on volume control valve 185 for pipeline 181, wherein, according to an embodiment as an alternative solution, volume control valve 185 in fact also can be configured with two connecting ends separated 199,201 as three-position five-way Proportional valve.In order to understand better, form of implementation below relates to shown configuration, wherein, it is envisaged that connecting end 199 and 201 really only relates to the connecting end of a corresponding conversion.Connecting end 203 is connected with pipeline 213, and described pipeline leads to storage tank 3 by filter-press 215.Bypass 217 cross-over connection of the pressure difference valve 219 that filter-press 215 is opened by the direction had towards storage tank 3.
The connecting end 205 of volume control valve 185 is connected with the cooling unit 221 in particular for first clutch K1.Connecting end 207 is connected with the second cooling unit 223 in particular for second clutch K2.
In the first shown in FIG ultimate state of volume control valve 185, connecting end 201 is connected with connecting end 203, and connecting end 199,205 and 207 is changed obstructed.Therefore the whole hydraulic fluid flow flowing through cooler 183 in other words that flow in hydraulic pipe line 181 are directed in pipeline 213 by connecting end 201,203, are directed in storage tank 3 thus by filter-press 215.
In the second ultimate state, connecting end 199 and 205 is connected to each other, and connecting end 201,203 and 207 is changed obstructed.In a state in which, the whole hydraulic fluid flow arriving volume control valve 185 are supplied to the first cooling unit 221.
In the 3rd ultimate state of volume control valve 185, connecting end 199 and 207 is connected to each other.Connecting end 201,203 and 205 is changed obstructed.Accordingly, in a state in which, in pipeline 181, whole hydraulic fluid flow of flowing are supplied to the second cooling unit 223.
As described, volume control valve 185 is configured to Proportional valve, and thus, the intermediateness adjustable between described ultimate state, thus, can be adjusted to cooling unit 221,223 or mention the volume flow of filter-press 215.Also work with can making volume control valve 185 beat, wherein, take described three ultimate states respectively in short time one of at least.Also control in this working forms time average or regulate guiding guide in other words to filter-press 215 to cooling unit 221,223 and guide thus to the volume flow of storage tank 3.
Fig. 1 illustrates, except the hydraulic fluid flow existed in pipeline 181, the hydraulic fluid flow of pipeline 57 can add and be supplied to hydraulic subsidiary loop 59.As an alternative solution, also only pipeline 57 feed-in hydraulic medium can be given.Also need it is to be noted that especially opposing spring force electricity proportion adjustment Proportional valve 101,101 ', 141,159,159 ', 179,179 ', 185 can be distinguished.
As already described, pipeline 57 leads in hydraulic subsidiary loop 59, exactly, leads in pipeline 181 in pump 9 downstream.According to as an alternative solution in this unshowned form of implementation, pipeline 57 preferably leads in pipeline 181 in cooler 183 downstream.According to form of implementation as an alternative solution, by hydraulic medium being fed in hydraulic subsidiary loop 59 from high tension loop, reduced by the total volume stream of cooler 183.Reduced by volume flow, reduced by the Pressure Drop of cooler 183, thus, the driving-energy needed for pump 7 and/or 9 reduces.Therefore, hold up power by reducing speed, the driving-energy needed for motor 5 reduces.Speed hold up power in other words stress level reduce abundant time---with how to reduce to have nothing to do, propose according to another form of implementation, pump 9 is directly connected with motor 5, namely removes shown disengaging coupling 11.
Propose according to another form of implementation in this unshowned layout about filter-press 215, described filter-press is not be arranged in pipeline 213 between volume control valve 185 and storage tank 3, but be preferably arranged in pipeline 181, especially between cooler 183 and volume control valve 185.Lead in pipeline 181 in filter-press 215 downstream at this preferred pipeline 57.By the setting type as an alternative solution of filter-press 215---described filter-press is in the main flow of hydraulic medium now, time quantum improves---and within described time quantum, hydraulic medium is filtered by filter-press 215.By-pass valve 219 preferably holds up power to design according to the minimum speed of volume flow at this.
As shown by volume control valve 185 and the alternative of the form of implementation described, propose according to another form of implementation, preferably convert dislocation like this, connecting end 199 and/or 201 in the first ultimate state is connected with connecting end 205 or 207, all the other connecting ends of volume control valve 185 are changed obstructed, in the second ultimate state, connecting end 201 and/or 199 is connected with connecting end 203, all the other connecting ends are changed obstructed, in the 3rd ultimate state, connecting end 199 and/or 201 is connected with connecting end 207 or 205, and all the other connecting ends are changed obstructed.Avoid by converting dislocation like this controlling volume control valve 185 to have volume flow also to flow to another clutch K2 K1 in other words when adjusting the hydraulic fluid flow expected for one of clutch K1 or K2 at beat.Replace, the volume flow not being channeled to corresponding clutch K1 or K2 when beat is directed in storage tank 3.When in fact volume control valve 185 is configured to 3-position 4-way Proportional valve, connecting end 199 and 201 is interpreted as the public in other words unique connecting end of pipeline 181 on volume control valve 185 all the time, thus, in fact only one of described two connecting ends 199,201 are arranged on volume control valve 185.
Fig. 2 and Fig. 3 partially illustrates the simplification view of the oil hydraulic circuit 1 according to a preferred development configuration.Identical reference number is provided with, therefore, thus with reference to description above by the figure of the known element of Fig. 1 below.
Be with the main distinction of above-described embodiment, oil hydraulic circuit 1 comprises a hydraulic subsidiary loop 225 now, and described hydraulic subsidiary loop is substantially for operating parking blocking device 227.Parking blocking device 227 comprises the final controlling element 229 of hydraulically operable, described final controlling element comprises the piston 233 that can be kept in cylinder 231 axially displacedly, wherein, piston 233 at one end forms parking blocking element 235 and forms holding member 237 at the other end, described parking blocking element can be placed to be linked into parking blocking device in speed changer, and described holding member configures to holding device 239.Holding device 239 has electromagnet 241, and described electromagnet acts on locking mechanism 243.Locking mechanism is embedded in the bite of holding member 237, so that the pressure making piston 233 keep out Returnning spring 245 remains in the position exited and unlock in other words.By operation electromagnet 241, be preferably configured as the right locking mechanism of gripping arm 243 in the current situation and close, wherein, pass through produced magnetic force, gripping arm swings in other words to move toward one another, to be engaged the bite of holding member 237.If electromagnet 241 changes to obtain no current, then gripping arm is to opening, and thus, holding member 237 is released and piston 233 is squeezed by Returnning spring 245 towards the direction of holding member 235 and is shifted in other words, to make speed changer locking.Also can consider as an alternative solution to construct holding device 239 like this, make gripping arm namely carry out current load to by operating electromagnet 241 and open, and electromagnet 241 change no current time stay only in its occlusal position.In the side opposed with Returnning spring 245, form hydraulic pressure cavity, described hydraulic pressure cavity is connected with by pressure accumlator 53 and pressure source 249 that at least pump 7 is formed by conversion equipment 247.
In the present example, conversion equipment 247 is connected in pipeline 73.At this, conversion equipment 247 has the first changing valve 251, and described first changing valve is configured to two-position three way changing valve.For this reason, described first changing valve has the first connecting end 253, second connecting end 255 and the 3rd connecting end 257.First connecting end 253 is connected with pressure piping 73 by filter-press 259 at this.Connecting end 255 is connected with storage tank 3, and connecting end 257 is connected with pipeline 261, and described pipeline leads to final controlling element 229 its pressure chamber in other words.Separate pipeline 263 from pipeline 261, this pipeline leads in pipeline 83, separates pipeline 81 and 85 from this pipeline.Before assigning in pipeline 263, in pipeline 261, changing valve 251 downstream is provided with another filter-press 265.Pipeline 263 forms the continuation of the pipeline 73 in Fig. 1 at this.
Changing valve 251 can electricity ground, especially electromagnetic ground operation, wherein, described changing valve can overcome the power of Returnning spring and the Pressure-induced Shifts optionally additionally or as an alternative solution by means of the pressure piping 74 separated from pipeline 79 resisted in pipeline 73 electricly.But also can consider pneumatically as an alternative solution or hydraulically operation transformation valve 251.In the first shown limit position in other words in the first ultimate state, even if changing valve 251 makes connecting end 257 be connected with storage tank 3 with connecting end 255 final controlling element 229, thus, final controlling element 229 is changed without pressure.In this state, as long as operated for the electromagnet 241 opening locking mechanism 237, piston 233 just can be displaced in its locked position of coupler.
In its second ultimate state, changing valve 251 makes connecting end 253 be connected with connecting end 257, and thus, the hydraulic medium from pressure source 249 is supplied to final controlling element 229 and pressure regulator valve 101,141 and 101 '.If therefore operation transformation valve 251, then build-up pressure on the side opposed with Returnning spring 245 of piston 233, described pressure makes piston 233 be shifted towards the direction of holding device 239.In this way, the parking blocking device 227 be previously linked into unclamps and exits in other words.The end of the formation holding member 237 of piston 233 is constructed by frustum-like shape, described end is squeezed between the gripping arm of locking mechanism 243, described locking mechanism arrives in occlusal position preferably by carrying out current load to electromagnet 241, to remain in the position exited with making piston 233 positive, even if the pressure in pressure chamber is cancelled.
Because pressure regulator valve 101,101 ' is connected with pressure source 249 with 141, so can carry out conversion and the joint of dual-clutch transmission now simultaneously.In order to be linked into parking blocking device 227, make changing valve 251 arrive in its first ultimate state, thus, pressure regulator valve 101,101 ' and 141 and final controlling element 229 are changed without pressure.In addition, if correspondingly operate holding device 239, be then linked into parking blocking device and therefore make speed changer locking, and no longer can carry out engaging and changing.
Fig. 3 shows the favourable expanded configuration of of form of implementation shown in Fig. 2, wherein, be connected to pressure regulator valve 159,179 and 159 ', 179 ' pressure regulator valve 141 before to be directly directly connected with pressure source 249 thus with pipeline 73 by pipeline 85.In addition, this form of implementation is corresponding to previously described form of implementation.Realize thus: if parking blocking device 227 is converted without hydraulic pressure, as shown in Figure 3, be connected to gear regulator 155,155 ', 157,157 ' pressure regulator valve 141 before to be also connected with pressure source 249, thus, although convertible, one of clutch K1 or K2 can not be made to close.Thus, according to present example, if if parking blocking device can exit and exit changing valve 251 in other words in other words and be displaced in its first ultimate state, only subfunction hydraulic subsidiary loop that only namely hydraulic subsidiary loop relates to clutch K1, K2 is in other words deactivated.
Fig. 4 shows the detailed view of one of conversion equipment 247 form of implementation as an alternative solution.Different from the conversion equipment shown in Fig. 2 and Fig. 3, at this, changing valve 251 has an other connecting end 267, and described other connecting end is connected with storage tank 3.Thus, in the first ultimate state, as shown in Figure 4, changing valve 251 also makes pressure piping 73 be connected with storage tank 3, and consequently, pressure accumlator 53 is drained off-load in other words.Ensure thus, in off state, also must desirably exit parking blocking device 227.Therefore, the misoperation of changing valve 251 can not cause piston 233 to resist the Pressure-induced Shifts of Returnning spring 245.In the second ultimate state, both connecting ends 267 and 255 are changed obstructed.Correspondingly, as an alternative solution or additionally, the second changing valve 269 also can be configured with the other connecting end leading to storage tank 3.
Fig. 5 and Fig. 6 shows an embodiment as an alternative solution, and in the described embodiment, conversion equipment 247 also comprises the second changing valve 269 except the first changing valve 251.Second changing valve 269 is preferably also configured to two-position three way changing valve and has connecting end 271,273 and 275 for this reason, wherein, connecting end 271 is connected with pipeline 279 by filter-press 277, and connecting end 272 is connected with storage tank 3, and connecting end 275 is connected with pipeline 261.Pipeline 279 separates from pipeline 49 and is connected in parallel with pipeline 73 thus.Changing valve 269 preferably electrically actuatable, but also can construct can pneumatic or hydraulic operation.Its structure is substantially corresponding to the structure of the changing valve 251 according to above-described embodiment.
Separate pipeline 281 from pipeline 261 in filter-press 265 downstream, described pipeline leads to the valve face 283 of the first changing valve 251.If valve face 283 is loaded pressure, then changing valve 251 is displaced in its second ultimate state, and in described second ultimate state, connecting end 253 is connected with connecting end 257.At this, connecting end 257 is connected with pipeline 83 by pipeline 285, from this pipeline as previously separated pipeline 81 and 85 from pipeline 263.Second changing valve 269 is thus as the pilot valve being used for the first changing valve 251.In its shown first limit position, the second changing valve 269 makes connecting end 275 and 272 be connected to each other, and thus, final controlling element 229 is changed without hydraulic pressure.In its second limit position, changing valve 269 makes connecting end 271 and 275 be connected to each other, and thus, the hydraulic medium being loaded pressure from pressure source 249 is supplied to final controlling element 229 and parking blocking device exits.Meanwhile, pressure is directed on valve face 283 by pipeline 281, and thus, the first changing valve 251 is operated and is displaced in its second limit position, and in described second limit position, connecting end 253 and 257 is connected to each other.Thus, in the current situation, pressure regulator valve 101,101 ', 141 is connected with pressure source 249, thus, can perform conversion and engaging process in other words.If parking blocking device 227 is linked into, namely changing valve 269 is displaced in its first ultimate state, pressure on the valve face 283 of then the first changing valve 251 is also cancelled, thus, described first changing valve is shifted due to the reposition force of Returnning spring and turns back in its first ultimate state, thus, pressure regulator valve 101,101 ' and 141 is also changed without pressure.The advantage described before obtaining thus.By arranging the second changing valve 269 as pilot valve, the reliability of whole system significantly improves.In addition, the first changing valve 251 is operated without the need to electricity.Conversion equipment 247 only comprises an exercisable changing valve 269 thus according to this embodiment, thus, operates two changing valves by operation transformation device 247, but obtains identical result when reliability improves as before.Also realize by arranging the second changing valve 269: two changing valves can be configured to the application target corresponding with it and coordinate mutually to mate in other words.
Fig. 6 shows one of the expanded configuration shown in Fig. 5 form of implementation as an alternative solution, in described form of implementation, pressure regulator valve 141 is also directly connected with pipeline 73 by pipeline 85, thus, by the only deexcitation or activate a hydraulic subsidiary loop subfunction in other words of dual-clutch transmission simultaneously of operation parking blocking device.In the case, the clutch of dual-clutch transmission is changed without pressure when being linked into Parking Brake simultaneously, and have nothing to do with the conversion attitude/position of pressure regulator valve 141.Certainly also can consider, before multiple second pressure regulator valve is connected to gear regulator and after conversion equipment 247, wherein, then described second pressure regulator valve one of at least, preferably whole second pressure regulator valve change without pressure when being linked into Parking Brake.
Claims (14)
1. a clutch speed-changer, described clutch speed-changer has at least one shift transmission, described shift transmission comprises energy hydraulically operated clutch (K1, K2) and at least one can hydraulically operated gear regulator (155, 157, 155 ', 157 '), described clutch speed-changer has oil hydraulic circuit (1), described oil hydraulic circuit comprises the pressure source (249) providing the storage tank of stress-free hydraulic medium (3) and provide the hydraulic medium being loaded pressure, wherein, in order to operate corresponding clutch (K1, K2) before the clutch of described correspondence, connect one first pressure regulator valve (101 respectively, 101 ') and at the gear regulator (155 of correspondence, 157, 155 ', 157 ') at least one second pressure regulator valve (141) is connected before, wherein, described pressure regulator valve (101, 101 ', 141) conversion equipment (247) that at least one pressure regulator valve and in is connected to above is connected, and described conversion equipment makes this at least one pressure regulator valve (101,101 ', 141) with one can be connected with described pressure source (249) or is connected with described storage tank (3) by hydraulically operated parking blocking device (227).
2. clutch speed-changer according to claim 1, is characterized in that: described first pressure regulator valve (101,101 ') and/or described second pressure regulator valve (141) are connected with described conversion equipment (247).
3. according to the clutch speed-changer of claim 1 or 2, it is characterized in that: described conversion equipment (247) has at least one first changing valve (251), described first changing valve is upper and described pressure regulator valve (101,101 ' at the first connecting end (257); 141) connect, be above connected with described pressure source (249) at the second connecting end (253), and be above connected with described storage tank (3) at the 3rd connecting end (255).
4. clutch speed-changer according to claim 3, is characterized in that: first connecting end (257) of described first changing valve (251) is also connected with described parking blocking device (227).
5. clutch speed-changer according to claim 3, it is characterized in that: described conversion equipment (247) has the second changing valve (269), described second changing valve is connected with described pressure source (249), described storage tank (3) and described parking blocking device (227), wherein, described second changing valve (269) configures to described first changing valve (251) as pilot valve.
6. clutch speed-changer according to claim 4, it is characterized in that: described conversion equipment (247) has the second changing valve (269), described second changing valve is connected with described pressure source (249), described storage tank (3) and described parking blocking device (227), wherein, described second changing valve (269) configures to described first changing valve (251) as pilot valve.
7. clutch speed-changer according to claim 4, it is characterized in that: be at least the changing valve (251 be connected with described parking blocking device (227), 269) there is Returnning spring, described Returnning spring is by described changing valve (251,269) exclusion is in the first limit position, in described first limit position, described parking blocking device (227) is changed be connected with described storage tank (3) without pressure in order to it.
8. clutch speed-changer according to claim 6, it is characterized in that: be at least the changing valve (251 be connected with described parking blocking device (227), 269) there is Returnning spring, described Returnning spring is by described changing valve (251,269) exclusion is in the first limit position, in described first limit position, described parking blocking device (227) is changed be connected with described storage tank (3) without pressure in order to it.
9. according to the clutch speed-changer of claim 1 or 2, it is characterized in that: at least one second pressure regulator valve (141) described is directly connected with described pressure source (249).
10. clutch speed-changer according to claim 4, it is characterized in that: be at least that the changing valve (251) be connected with described parking blocking device (227) has at least one valve face (283), described valve face is connected with described pressure source (249) to regulate pressure to return impulse power in other words.
11., according to the clutch speed-changer of claim 1 or 2, is characterized in that: described pressure source (249) comprises at least one can the pressure accumlator (53) of motor-driven pump (7,9) and/or at least one hydraulic pressure.
12. clutch speed-changers according to claim 4, it is characterized in that: be at least the changing valve (251 be connected with described parking blocking device (227), 269) described pressure source (249) is made to be connected with described storage tank (3), if described parking blocking device (227) is also connected with described storage tank (3).
13. clutch speed-changers according to claim 6, it is characterized in that: be at least the changing valve (251 be connected with described parking blocking device (227), 269) described pressure source (249) is made to be connected with described storage tank (3), if described parking blocking device (227) is also connected with described storage tank (3).
14. clutch speed-changers according to claim 1, is characterized in that: described clutch speed-changer is double-clutch speed changer.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102011100857A DE102011100857A1 (en) | 2011-05-06 | 2011-05-06 | Double clutch |
| DE102011100857.1 | 2011-05-06 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102777592A CN102777592A (en) | 2012-11-14 |
| CN102777592B true CN102777592B (en) | 2015-04-08 |
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ID=45999540
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210137885.0A Active CN102777592B (en) | 2011-05-06 | 2012-05-04 | Double clutch transmission |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US8915344B2 (en) |
| EP (1) | EP2520832B1 (en) |
| CN (1) | CN102777592B (en) |
| DE (1) | DE102011100857A1 (en) |
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| DE102012021598B4 (en) | 2012-10-30 | 2017-12-07 | Audi Ag | Switching device for a dual-clutch transmission |
| DE102013003894A1 (en) * | 2013-03-06 | 2014-09-11 | Audi Ag | Hydraulic system for a dual-clutch transmission |
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| DE102013222985A1 (en) * | 2013-11-12 | 2015-05-13 | Zf Friedrichshafen Ag | Automatic transmission with a hydraulic system for actuating a parking brake device and other hydraulically actuated modules |
| DE112016001271T5 (en) * | 2015-04-17 | 2018-01-18 | Borgwarner Inc. | MULTI-PRESSURE HYDRAULIC CONTROL SYSTEM FOR A STAGE-FREE VARIABLE AUTOMATIC TRANSMISSION |
| CN105443749A (en) * | 2015-12-15 | 2016-03-30 | 第一拖拉机股份有限公司 | Electric hydraulic control parking and locking mechanism of tractor |
| DE102016206561B4 (en) * | 2016-04-19 | 2019-03-21 | Zf Friedrichshafen Ag | Method for operating a parking brake device by means of a hydraulic system |
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| WO2018192989A1 (en) * | 2017-04-18 | 2018-10-25 | Punch Powertrain N.V. | A hydraulic system for a vehicle, a vehicle transmission, and method for operating a vehicle transmission |
| NL2018732B1 (en) * | 2017-04-18 | 2018-10-29 | Punch Powertrain Nv | a hydraulic system for a vehicle, a vehicle transmission, and method for operating a vehicle transmission |
| DE102017211025A1 (en) * | 2017-06-29 | 2019-01-03 | Zf Friedrichshafen Ag | Actuator arrangement |
| BE1025480B9 (en) | 2017-08-18 | 2019-04-08 | Punch Powertrain Nv | ELECTRICALLY CONTROLLABLE HYDRAULIC SYSTEM FOR A VEHICLE TRANSMISSION AND A METHOD FOR DRIVING THEM |
| DE102018214438A1 (en) * | 2018-08-27 | 2020-02-27 | Zf Friedrichshafen Ag | Hydraulic system for a transmission of a motor vehicle drive train |
| DE102018126549A1 (en) * | 2018-10-24 | 2020-04-30 | Fte Automotive Gmbh | Hydraulic clutch actuator |
| DE102020110610B4 (en) * | 2020-04-20 | 2022-08-11 | Audi Aktiengesellschaft | Method for operating a double clutch transmission of a motor vehicle and motor vehicle |
| CN113700856B (en) * | 2020-05-21 | 2022-08-19 | 广州汽车集团股份有限公司 | Hydraulic parking oil supply system of automatic transmission |
| DE102020004982A1 (en) * | 2020-07-15 | 2022-01-20 | Daimler Ag | Automatic transmission for a motor vehicle and motor vehicle |
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| DE4117736C1 (en) * | 1991-05-30 | 1992-05-21 | Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De | |
| WO2010083862A1 (en) * | 2009-01-23 | 2010-07-29 | Daimler Ag | Hydraulic control device for an automated transmission |
| CN101900202A (en) * | 2008-10-21 | 2010-12-01 | 通用汽车环球科技运作公司 | The control system that is used for dual-clutch transmission |
| CN102032339A (en) * | 2009-09-29 | 2011-04-27 | 通用汽车环球科技运作公司 | Hydraulic control systems for dual clutch transmissions |
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| DE19625019A1 (en) | 1996-06-22 | 1998-01-02 | Bayerische Motoren Werke Ag | Motor vehicle with an automatic transmission |
| JP2003021199A (en) * | 2001-07-06 | 2003-01-24 | Isuzu Motors Ltd | Rotation synchronizing mechanism for automatic clutch type transmission |
| DE102004033362B4 (en) | 2004-07-02 | 2007-05-16 | Getrag Getriebe Zahnrad | Hydraulic circuit for a dual-clutch transmission |
| DE202007014903U1 (en) * | 2007-10-24 | 2008-01-17 | Zf Friedrichshafen Ag | Electrohydraulic control device of a transmission device |
-
2011
- 2011-05-06 DE DE102011100857A patent/DE102011100857A1/en not_active Ceased
-
2012
- 2012-04-12 EP EP12002580.4A patent/EP2520832B1/en active Active
- 2012-05-04 US US13/464,154 patent/US8915344B2/en active Active
- 2012-05-04 CN CN201210137885.0A patent/CN102777592B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4117736C1 (en) * | 1991-05-30 | 1992-05-21 | Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De | |
| CN101900202A (en) * | 2008-10-21 | 2010-12-01 | 通用汽车环球科技运作公司 | The control system that is used for dual-clutch transmission |
| WO2010083862A1 (en) * | 2009-01-23 | 2010-07-29 | Daimler Ag | Hydraulic control device for an automated transmission |
| CN102032339A (en) * | 2009-09-29 | 2011-04-27 | 通用汽车环球科技运作公司 | Hydraulic control systems for dual clutch transmissions |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102011100857A1 (en) | 2012-11-08 |
| EP2520832A2 (en) | 2012-11-07 |
| US8915344B2 (en) | 2014-12-23 |
| CN102777592A (en) | 2012-11-14 |
| EP2520832B1 (en) | 2019-06-26 |
| EP2520832A3 (en) | 2016-06-29 |
| US20130118852A1 (en) | 2013-05-16 |
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